Winding machine



Dec. 28, 1937. Y Y J. c. ANDERSON 1 2,103,239

v wmniue MACHINE r Original Filed April 7, 1926 13 sheets-sheet 1 INVENTOR- JA MES C. A NDERSG/V, Deceqsed BY ANN/E G. ANDERSO/V, Extcufrzk I A TTORNEYS Dec. 28, 1937. lb. ANDERSON 2,103,239

WINDING MACHINE Original Filed April "I, 1926 13 Sheets-Sheet 2 IN VEN TOR.

JA MES C. A NDERSOM Deceased B Y A/V/V/ E G. A IVDER'SON, Execafrz'x E gATTORNEYS.

J. C. ANDERSON WINDING MACHINE I Original Filed April 7, 1926 13 Shets-Sheet s 1 N V EN TOR J11 ME 5 C ANDEAJWN, Debedsed B Y A Al/V/E 6. A NOE/F3041 Evert/fr):

TORN YS;

Dec. 28, 1937.

1 J. c.. ANDERSON WINDING MACHINE Dec. 28, 1937. J. c. ANDERSON WINDING MACHINE Original Filed April 7, 1925 13 Sheets-Sheet 5 JA MES c. A

guy/VI.

I INVENTOR NDERSO/KDeceased BY ANN/E G. ANDERSOM Executrb: 5 Y M A T ORNEYJ Dec. 28, 1937.

J. c. ANDERSON 2,103,239

WINDING MACHINE Original Filed April 7, 1926 13 Sheets-Sheet 6 IN V EN TOR.

JAMES C. A/VDERSO/V, BYA/V/V/E GANDERSO/V,

Deceased Ezecu Zr/Lt BY W a/& v TORNEYS.

Dec. 28, 1937. I J, c, A DERSON 2,103,239

WINDING MACHINE Original Filed April 7, 1926 15 Sheets-Sheet 7 INVENTOR. .JAME- CANDERSO/V, Deceased a Y A NN/E a. A NDEESO/V, Execa mar 24-8 I 4 9 9 BY M m In TTORNEYS. WWW

1 1 WINDING; MACHINE Oii'gifilfilgd April 7, 1926 13 Sheets-Sheet a INVENTOR JA MES C. ANDERSO/V, Deceased BY A Al/V/E G. ANDERSO/V, Exqcutr/Lr BY M M A TTORNEY6 Dec. 28, 1937. C ANDERSON 2,103,239

WINDING MACHINE Original Filed April 7, 1926 13 Sheets-Sheet 9 n h v INVENTORY a w Q S 3 3 JA/visamvomsalupemsed y A/v/v/E 6. ANDERSON, 518mm:

I ATTORNEYS Dec. 28, 1937. J. c'. ANDERSON WINDING MACHINE Original Filed April 7, 1926 13 Sheets-Sheet 10 d w. R

W. mm H H I. N e m l W wl 1 H n? m o Q\ I S Hp I m D N MN E N MR H m s u E M M m %&\ M

m 1 1 Naif \N .E

BY Mf M ATTORNEYS Dec. 28, 1937. N J. c. ANDERSON WINDING MACHINE Original Filed April 7, 1926 1,3 Sheets-Sheet 11 INVENTOR. JAMES C. ANDERSO Deceased.

Mk. Ru M Ec R w n Wm A M G F l l Dec. 28, 1937; J c ANDERSON 2,103,239

WINDING MACHINE Original Filed April 7, 1926 13 Sheets-Sheet 12 I WW JAMES CANOE/F80, Deceased BY A/V/V/E G. ANDERSON, Executrz'x ATTORNEYS Dec. 28 1937. J. c. ANDERSON WINDING MACHINE l5 Sheets-Sheet 13 Original Filed April '7, 1926 Patented Dec. 28 1937 UNITED STATES PATENT OFFICE WINDING MACHINE Application April 7, 1926, Serial No. 100,319 Renewed July 29, 1936 33 Claims.

This invention relates to machines for winding strands of material, such as wire, thread, ribbons or filaments into coils, helices or bobbins, and has special reference to machines for winding copper wire into electrical coils or helices for use in various kinds of apparatus. The particular invention herein described is an improvement upon machines described in U. S. Patents No. 654,583 issued July 31, 1900, and No. 798,864, issued September 5, 1905, with particular reference to the latter. In the patented machines mentioned, a plurality of coils are wound simultaneously. in separated zones. upon a spindle or mandrel, the convolutions of wire being wound in layers superimposed one upon the other and the machine being adapted to introduce or inject sheets of paper between the adjacent successive layers during the building-up of the coil and while the spindle is in motion. Each layer in all of the coils is finished 20 at the same instant, and at that instant a sheet of paper, of suflicient length to make one or more complete wrappings around each coil and of sufficient width to extend over all of the coils on the spindle, is delivered to the spindle and wound thereon as a foundation for the next succeeding layer. When the required number of layers are completed the machine stops and all of the coils on the spindle are removed in a body or stick which is afterward separated into individual coils by severing the various layers of paper between the spaced coils.

The object of this invention is to provide a simplified general purpose strand winding machine which is readily adaptable to a wide range of work.

Among the improvements of the present invention over the aforementioned patented machines is the manner in which the paper is handled and introduced between the layers of the coils. The paper serving mechanism of the present invention comprehends a new and more desirable cycle of events, whereby the simultaneous winding of a comparatively large number of coils is effected by providing mechanism capable of feeding to the spindle, successive sheets of paper of suflicient width to cover the comparatively large number of coils on the spindle,'and to inject those sheets into the coils and windthem thereupon evenly and smoothly without diminution of the spindle speed to furnish individual foundations for the respective layers of wire. Means is also provided whereby a plurality of different sources of sheet material supply is furnished, any one of which may be readily selected during and without interrupting the winding process. For example, the

first and last few layers of all of the coils of a winding can be served, if desired, with heavy paper, oiled linen, silk, or the like, and the intervening layers may be served with an insulating paper adequate for the purpose, which is accom- 5 plished selectively while maintaining the spindle speed, without wrinkling the sheet layers or producing other irregularities therein, notwithstanding the fact that exceedingly thin paper may be used.

Another improvement over the aforementioned patents, particularly No. 798,864, is the replacement of the reciprocating slide, carrying the knife and paper feeding devices, by a pair of light oscillatory pivoted paper carrying arms which draw the paper over a support or platen and operate in conjunction with a severing and measuring mechanism to serve smoothed sheets of the proper size to a paper ejecting mechanism which thereafter inserts the sheets into the grip of the strands being wound upon the revolving spindle. More specifically, the paper gripping fingers, at the extremities of the pivotedarms, grasp the lateral margins of the paper web near the forward edge and effect a slight lateral motion and draw it taut on the support or platen as well as along its forward edge, feed an automatically measured length of the web through a relatively stationary knife, pause while the sheet is severed from the web by the knife, resume the feed, and deliver the sheet by transferring its forward edge to the ejector mechanism, whereupon the lateral gripping fingers are immediately rapidly retracted, the sheet being supported on and constrained to the surface of the platen by independent pressure members as well as by gravity instead of being solely suspended from one edge and otherwise left free to obtain what support is within reach. Accordingly, smooth and eflicient operation is obtained within a small compass, whereby the friction, inertia, and momentum of the massive reciprocating slides of former machines is eliminated, as well as much of the size and cost of the machines.

The mechanism for feeding the strand material, such as wire, is substantially the same as that disclosed in aforementioned Patent No. 198,864, as well as the wire feed reversing mechanism, whereby the successive layers of wire are wound at the proper predetermined length with a reciprocatin'g movement upon each other and severally along the spindle in the usual manner, with the addition of a selective mechanism for automatically contracting the length of each successive layer in order to make another type of finished coil 55 erence to the coils being wound, is superior to the previous types of machines in that all of the,

wire on and passing from all of the spools is directly visible to the operator standing in front. of the machine, and in that all of the spool axes are very nearly horizontally arranged to avoid snarling when unwinding, the slight angle to the horizontal being only of such an amount and direction to prevent the spool from falling or flying off of its arbor should the spool locking devices suddenly fail, and the spools, being mounted on overhung arbors, are accordingly readily taken off and replaced from the sides of the machine without interfering with the neighboring spools or the strands of wire passing therefrom to the winding spindle.

By utilizing a trunnion-pivoted carriage, the machine is adaptable to wind a wide range of coil diameters, and the driving mechanism includes gearing and pulleys that can be selectively engaged to drive the winding spindle at the requisite speeds consistent with the diameter and character of coils to be wound. For example, in wind ing relatively small diameter coils, belt driven cone pulleys are utilized whereby relatively higher speeds are attainable with comparative silence and negligible vibration, and in winding heavier wire and larger coils, for which slower speeds and greater power may be necessary, intermeshing spur gear combinations are provided. In order to eliminate the complication attending the utilization of a plurality of cam-operated friction clutches, the present machine employs only one friction clutch in conjunction with several small jaw clutches, which latter are liable to but little wear, and consequently need very rarely if ever to be replaced, whereas friction clutches need periodic attention for adjustment, relining and the like.

A back-winding system is provided on the present machine, which resembles that described in aforementioned Patent No. 798,864, whereby the arbors of the wire supply spools are driven by the winding spindle mechanism in a direction opposite to that which they are revolved by the unwinding of the wire as it is being drawn off of the spools and wound upon the winding spindle. Accordingly, by manually effecting the clutching of reversing gears in the present machine, the winding spindle and the spools are dependently driven in a reverse direction to unwind wire from the winding spindle and to rewind it upon the several spools, in order to return the machine to a prior position in the winding process for the purpose of mending a broken strand, replacing an exhausted spool, or the like.

The particular nature of the invention as well as the objects and advantages thereof will appear more clearly from the following description of a preferred embodiment as illustrated in the accompanying drawings, in the several views of which like reference characters designate like parts.

In the drawings:

Fig. 1 is a front elevation of the coil winding machine;

Fig. 2 is a plan view thereof, with the spool frame removed;

Fig. 3 is a side elevation of the machine shown in Fig. 1, the upper portion of the spool frame being broken away;

Fig. 3a shows a continuation, in side elevation, of the broken away spool frame of the preceding if desired. The arrangement of the wire supply spools and the tensioning mechanism, with ref- Fig. 4 is a perspective view of the main drive and associated shafting and other parts, as viewed from the rear of the machine from the normally right hand side thereof toward the center;

Fig. 4a is complementary to Fig. 4 and shows the continuation of the main drive and allied shaftin'g to the normally left hand side of the machine;

Fig. 4b is complementary to Fig. 4 and shows the interchangeable gears for changing the backwinding speed;

Fig.5 is a plan view showing associated shafts in a drive in which the ratchet mechanism is included;

Fig. 6 is a detail view of a ratchet drive;

Fig. 7 is a vertical section showing the internal arrangement of the parts of the right hand side of the machine;

Fig. 8 is a similar view, but shows the parts on the left hand side of the machine;

Fig. 8a is a complementary view to Fig. 8 showing the paper ejecting actuating mechanism;

Fig. 9 is an irregular generally vertical section through the right hand side of the machine, the paper conveying arm having been arbitrarily moved into its upper position;

Fig. 10 is a corresponding view through the left hand side of the machine;

Fig. 11 is a detail view showing an oscillatory lever, partly in section, which is included in a linkage which is operable to shift the cams in the cam housing;

Fig. 12 is a perspective view of the upper end of one of the paper carrying arms, showing the relation of the stationary and movable fingers;

Fig. 13 is a fragmentary vertical section through the cams and cam housing that are attached to the right hand wall of the carriage frame;

Fig. 14 is a detached view showing the switch cam and the parts which coact therewith;

Fig. 15 is a detached view of the knife cam;

Fig. 16 is a similar view of the gripper cam;

Fig. 17 is a rear elevational view of the lower portion of the machine, as viewed in the direction of the arrow A in Fig. 7;

Fig. 18 is a fragmentary projection of the lower portion of the mechanism shown in Fig. 7, as viewed in the direction of the arrow B;

Fig. 19 is a view of one of the paper shield plates of the switch mechanism;

Fig. 20 is a similar view of another of such shields;

Fig. 21 is a like view of one of the supplementary guide plates which is associated with each of the shields;

Fig. 22 is another such auxiliary guide plate. such as is centrally positioned with respect to the shields;

Fig. 23 is a fragmentary front elevational view of the carriage, showing in its upper portion means for adjusting the ejector plate, said view also showing in its lower portion a supporting bar for the paper shield spiders;

Fig. 24 is a sectional detail showing means for adjusting the fulcrum of a feed actuated arm;

Fig. 25 is a sectional detail of a clutch associated with a shaft which is adjustable with respect to a number of layers in a prescribed coil;

Fig. 26 is an irregular section through the head stock, a portion of the exterior of the latter being shown in elevation;

Fig. 27 is a view taken at right angles to head stock as shown in Fig. 26, certain of the parts being broken away for improved clearness;

Fig. 28 is principally a section through the tail stock;

Fig. 29 is a view of the tail stock as seen at right angles to the view in Fig. 28, portions being in section;

Fig. 30 is a detailed section fication of the tail stock center;

Fig. 31 is a sectional detail view of locking means for the tail stock;

Fig. 32 is a plan view of the spool frame, showing in dotted lines the rewinding mechanism for the spools;

Fig. 33 is a detail view of a part of the rewinding mechanism showing the grouping and unification of certain gears;

Fig. 34 is a longitudinal section illustrating certain braking mechanism associated with individual spools;

Fig. 35 is an end view of the braking mechanism; and

Fig. 36 is a diagrammatic view, in perspective, showing the pitch circles of the gears in the rewinding mechanism together with shafts that connect various gears.

Referring to thedrawings, and particularly to Figs. 1 and 3, numerals l and 2 designate the standards comprising the pedestal which supports the bed plate 3 of the machine. The power is furnished by a motor 4, as illustrated in Fig. 3, or any other driving means, which, by a belt 5 showing a modidrives clutch pulley 6 freely upon shaft 1 which is suspended from the'rear of bed plate 3 by means of hangers 8 and 9, as is most clearly illustrated in Figs. 4 and 4a. In order to drive shaft 1, starting handle H1, at the front of the machine, is thrown downwardly to turn clutch shaft II and lever |2 so as to move collar l3 in its keyway along shaft 1 to effect the engagement of clutch band M with clutch pulley 6, which accordingly drives pulley 6, since band I4 is pivoted on clutch slide |5 which is keyed to shaft 1. As'handle i9 is thrown downwardly into the clutching position shown in Fig. 1, coil spring I6 is tautened and the pawl ll of trip handle l8 engages an angular extension |9 upon handle H) which looks it in clutched position. Accordingly when it is desired to deolutch the machine from the power, it is only necessary to strike trip handle l8, Whereupon its pawl |1 releases clutch handle H], which is thrown upwardly against stop 20 by spring l6 to release clutch pulley 6 and stop the machine.

A normally closed jaw clutch 2|, keyed to shaft 1, rotates bevel pinion 22 which drives bevel gear 23 and shaft 24 which is journalled in hanger 8, as is illustrated in Fig. 4. A worm 25 is mounted on the other end of shaft 24 which rotates worm wheel 26 and consequently shaft 21 which is journalled on top of bed plate 3, as shown in Figs. 2 and 3. Referring to the enlarged views of Figs. 5 and 6 of the ratchet driving mechanism mounted on top of bed plate 3 in brackets 28 and 29, it will be seen that shaft 21, by virtue of ratchet 30, can only drive pinion 3| in one direction, namely in a counter-clockwise direction as viewed in Fig. 6, since the ratchet teeth in wheel 32 are arranged so-that pawl 33 engages them only when driven in that direction and is disengaged when pinion 3| is rotated in the opposite direction. It may be noted that the ratchet is only utilized when hand-wheel 36 is revolved when the machine is idle. Pinion 3| drives gear wheel 34, which is keyed to ashort shaft 35, as is hand-wheel 36, the other end of shaft 35 being formed with an integral disc 31 which constitutes the driving element of a slip coupling 38, which drives a coaxial shaft 39 through friction washers 48, which engage disc 31 and accordingly actuate member 4| pinned to'shaft 39, as illustrated in Fig. 5. A coil spring 42 maintains the proper pressure of washers 40 upon disc 31. By means of two universal joints 43 and 44, and two short shafts 45 and 46 connected to shaft 39, a pinion 41 is driven, which is journalled in right hand side frame 48.

The two side frames 48 and 49, illustrated in Figs. '7 and 8, respectively, are suspended in a space in the center of bed plate 3, being movably trunnioned upon shaft 50, which is mounted on brackets 5| and 52 secured upon and near the rear edge of bed plate 3. Referring again to Fig. 7, it will be seen that pinion 41 meshes with and drives gear 53 in a counterclockwise direction freely upon shaft 54, and which in turn drives gear 55 in a clockwise direction. A roller 56, attached near the edge of gear 53, moves in a rectilates about pin 58 as roller 56 describes its circular orbit and carries lever 51 with it. The lower end of oscillatory lever 51 is' provided with a toothed sector 59 which meshes with a pinion 68 causing it to periodically reverse in direction of.

rotation as it is driven by oscillating sector 59. Upon examining Fig. 9 in conjunction with Fig. 7, it will be seen that pinion 60 rotates freely upon a short shaft 6| and that embracing and rigidly pinned to it is a hub 62, which is illustrated as an enlarged plan view in Fig. 11. Hub 62 is provided with a slotted radial extension 63 having a pair of opposed ears 64 at its base between which is fulcrumed a double lever 65, the surface of the upper arm of which is bevelled, as shown in Fig. 11, and coacts with a similarly bevelled T-shaped lug 66 rigidly secured on lever 61 which is mounted freely upon the hub of pinion 60. Accordingly, upon the engagement of lever 65 with lug 66, a wiping cam effect is produced which causes lever 65 to pivot about its fulcrum in hub 62, which movement is constrained by pin 68 and spring 69, and consequently lever 65 efiects the movement of pin 16 longitudinally for purposes to be explained hereinafter.

The rotation of pinion 60 turns the hub of pinion 60, the hub 62, the extension 63 of the latter and pin 1|. on 63, which is engaged by a spring-pressed hook latch 12 pivotally mounted on arm 13, and so causes the rotation of arm 13 which is pinned to shaft 6| as illustrated in Figs. '7 and 9. Inasmuch as tubular shaft 14 is likewise pinned to shaft 6| and arm 13, and as the arms 13 and 15 are joined by tubular member 16,, a simultaneous motion is imparted to shaft 11 and arm 15 which are similarly mounted as illustrated in Fig. 10, the complement of Fig. 9. For purposes of clarity, arms 13 and 15 are shown respectively in a different position in Figs. 9 and 10 than that in which they are shown in Figs. '7 and 8. Arms 13 and 15 each terminate in a relatively stationary member 18 which is shaped as shown most clearly in Fig. 12 and is provided with a flat finger 19. The outer ends of arms 13 and 15 terminate in integral plates 86, each of which has a portion of reduced thickness, whereby a shoulder is formed longitudinally of the plate 80, as at in Fig. 12. To the portion of reduced thickness of each plate 89, a a

bent portion of the stationary member 18 is secured, so that it is parallel to but spaced from the shoulders 89. A retaining plate 86 which is shown broken away in Fig. 12, lies against a face of the thicker portion of the plate 89 of linear groove in lever 51, which accordingly oscilarms 13 and 15, and, as shown in dot and dash lines in Fig. 12, has a width approximating that of plate 88, the retaining plates 88 being secured by screws 88 to the plate-like termini 88 of the arms 13 and 15. Thus, the stepped plate 88 of each of these arms, the portion of stationary member 18 that parallels the shoulder 88*, the shoulder itself and the retaining plate 88 form a guide-way in each of the arms 13 and 15. In these guide-ways, radially movable members 8| and 82 are respectively provided, each of which terminates in a finger 83 disposed in juxtaposition to and adapted to coact with finger 18, which is rigidly secured to its associated arm 13 or 15. The end of finger 83 is provided with a friction block 84, which is pivotally and eccentrically mounted so that the closure of fingers 18 and 83 causes a lateral force component to move the block 84 in a lateral direction as the fingers 18 and 83 come together, and a consequent relative movement is produced between the coacting surface of block 84 and fiat finger 18. The lower extremity of slidable member 8| is pivoted to one end of a lever 85, the other end of which embraces and is pinned to the end of tubular bar 18, and a rigid stud 8| is mounted on the left-hand slidable member 8| only. Coil springs 88, one end of each of which is respectively attached to members 8| and 82 and the other respective ends to arms 13 and 15, tend to force the closure of fingers 18 and 83 which, however, is normally prevented by the angular position of bar 18 except at certain definite times, which are to be disclosed hereinafter.

Acting against the tension of springs 88 in order to hold fingers 18 and 83 apart during certain periods in the cycle, a spring-pressed curved pawl 81 engages a notch in slidable member 82 of arm 15, as is shown in Figs. 8 and 10, pawl 81 being pinned to one end of a short shaft 88 journalled in a tubular bearing 88 mounted integrally with arm 15, and a cam pawl 88 being pinned to the other end of shaft 88. Freely rotatable upon tubular shaft 14 is a lever 8|, held in place upon shaft 14 by a collar 82, and which bears a spring-pressed latch 83 which has the same axial location as pawl 88 and is adapted to engage therewith when arms 13 and 15 are in a certain angular position. Accordingly, as illustrated in Fig. 8, a certain definite angular movement of arm 15 away from lever 8|, causes latch 83, which is then engaged with pawl 88, to restrain the movement thereof, and since pawl 81 is attached to the same shaft 88 as pawl 88, it is moved away from slidable member 82, whereupon the latter is immediately retracted by spring 88 to close fingers 18 and 83 upon the lateral edges of a web of paper or other sheet material which is disposed so that the two pairs of fingers 18 and 83 embrace its lateral edges, but do not grip them until pawl 81 is released asabove described. Inasmuch as both slidable members 8| and 82 are attached through levers 85 to common shaft 18, they operate in unison, and, by the constraint of springs 88, fingers 18 and 83 of both arms 13 and 15 are closed simultaneously and stretch the paper laterally between them by the lateral sliding movement of members 84 upon fingers 18. The lever 8| has an additional purpose which will be explained hereinafter. A pinion 84 is pinned to shaft 11 and meshes with a gear 85 journalled on a stud 88 fixed in side frame 48, and gear 85 in turn meshes with pinion 81 adapted to rotate freely on stud 88,

and which is fixed to and actuates counterweight I88, and gear 55,

88 for the purpose of counterbalancing the mov ing masses of the reciprocating arms 13 and 15 and their complemental parts. Shafts 8| and 11, which are rigidly joined to tubular shaft 14 and to arms 13 and 15, respectively, are journalled on studs I88 and IIII in side frames 48 and 48, respectively, as illustrated in Figs. 9 and 10.

Having considered the condition where the arms 13 and 15 have been moved through a suflicient angle, by are 58 and pinion 88, so that the subsequent release of pawl 81 from its notch in slidable member 82 allows springs 86 to effect the closure of gripping fingers 18 and 83, the arms move freely through an arcuate path until the angular surface of pivotal lever 85, which moves with arm 13, engages the corresponding angular surface of relatively stationary member 88 with a wiping cam effect, whereupon a rocking movement is imparted to lever 85, as heretofore explained. The movement of lever 85 causes the lower portion thereof to exert an axial thrust which is imparted to pin 18, slidably mounted in bearing stud I88, which thrust effects the movement of lever I82, which is pivoted about a fulcrum plate I83 attached to side frame 48, as is illustrated in Figs. land 9. Referring now to Figs. 7 and 13, it will be seen that lever I82 is bifurcated at its other end so as to embrace the hub of cam I84, shown in Fig. 14, which together with gear 55, cam Figs. 15 and 16, is slidable against the restraint of spring I81 as well as rotatable upon a short shaft I88 which is mounted between side frame 48 and a triangular plate I88 attached to side frame 48 by means of three legs II8, III and H2. Accordingly, the movement of shifter lever I82 causes narrow-faced gear 55 to slide axially with respect to relatively broad-faced gear 53 with which it re mains engaged, and causes the consequent simultaneous disengagement of cam I84 from its follower roller II3, of cam I85 from its wiper follower II4 which is provided upon a pin II5 fixed in plate I88, and of cam I86 from itswiper follower II8 which is pivotally mounted upon a stud II 1 attached to plate I88, particular reference being made to Figs. 7, 9 and 13. Accordingly, during the period in the cycle of their disengagement, the cam followers II3, II 4 and' I I5 are disposed in the spaces provided therefor and shown to the right of their respective cams in Fig. 13. The cam disengagement, however takes place diu'ing the interval in which moving lever 85 engages T- shaped cam member 88, effecting the consequent movement of lever 85, pin 18, cam shifter lever I82 and the axial movement of cams I84, I85 and against the restraint of spring I81 which causes the return of the cam and gear unit subsequent to but not at the moment when lever 85 becomes disengaged from T-shaped member 88 to effect the engagement of cams I84, I85

and I 88 with their followers H3, H4 and II 8', re-

spectively. The delay in the engagement thereof being due to the fact that the cam followers, upon being disengaged from the cam faces, drop bebind the cam discs, which thereafter, because of greater radius, prevent the axial return movement of the cam and gear unit until the smallest radius of cam I85 permits the return of its follower I I4, and accordingly the reengagement of all of the cams under the pressure of spring I81, the cams being rotated by gears 53 and 55.

Approximately at the moment that lever engages T-shaped member 88, causing the disengagement of the cams as described above, a pin II8, upon hook latch 12, which has been moving arm I3 by virtue of its being hooked around pin I I upon lever 63 which is being driven by gear 60, engages spring-pressed pawl IIO, pivoted upon lever 61, which thereupon pries pin I I8 and consequently latch 12 radially outwardly to effect the unhooking of latch 12 from pin 1I. This results in the temporary arresting of paper carrying arms I3 and 15 at approximaely the moment that the cams are disengaged, and accordingly follower H6 is released from its cam I06 and is moved 1nwardly, i. e. toward the cam axis I08, which causes the movement of link I20, attached to the free end of follower I I6, the other end of the link being attached to one of levers I2I which are mounted upon a tubular shaft I22, the ends of which are journalled in the side frames 48 and 49. Two coil springs I23 are attached by one end to the side frames 48 and 49, and by the other end to levers I2I, so that they exert a tensional force upon levers I2I and link I20 and normally effect the constant pressure of follower H upon cam I06, as well as causing the downward movement thereof upon its being released from cam I00. The other ends of levers I2I are attached, by means of links I24, to a knife-carrying frame I25 which is freely slidable in angular guides I26 formed in side frames 48 and 49, as shown in Figs. '1 and 1'7. The triangular-shaped knives I21 are parallelly arranged and fixed to frame I25 by means of screws I28 so as to coact with anv l I20 to efiect a shearing action to sever the web of sheet material normally disposed between knives I21 and anvil I28 as springs I23 draw knifeframe I25 upon guides I26 when cam I06 is shifted by the tripping of lever 65. It is now apparent that when the paper is severed from the web, as above described, the paper carrying arms 13 and are temporarily stationary, after which they resume their travel. The paper carrying arms 13 and 15, having passed the point at which lever 65 engages T-shaped member 66, proceed as gear 60 continues to turn in a counter-clockwise direction, and accordingly to move oscillatory crank lever 51 which effects the movement of arm driving lever 83. The unhooking of latch 12 and pin II on arm driving lever 63 caused a temporary arrest in the travel of the paper carrying arms 13 and I5, which halt was for the purpose of severing the paper and was of a duration of time equivalent to the time required for pin 1| upon lever 63, which is continually moving, to catch up with a shoulder H in latch 12 thereby re-establishing the driving connection from lever 63 through latch 62 to the arm 13 which is thereupon driven forward as before.

As the paper carrying arms, proceed through their forward and upward are, but before their extreme forward position is reached, pin I30, upon rotating gear 53 engages lever I3I, which is pivotally mounted on a pin disposed on the side frame 48 and stopped against downward movement by a fixed stud I32, and moves lever I3I upwardly to move crank I33 which is pivotally mounted on a boss I34 on side frame 48. Such movement, resisted by coil spring I35, is transmitted by pull rod I36 to lever I31 and causes the rotation of rod I38, the ends of which are journalled in the side frames 48 and 49. The rotation of rod I38 causes contact roller I39 to actuate 1ever I40 about rod I4I as an axis, which is suspended at either end from rod I42 by means of a pair of levers I43. The angular movement of lever I40 raises ejector roll I44 away from plate I45 for an interval of time sufficient to permit the paper carrying arms 13 and 15 to insert the forward projecting edge of the sheet of paper or other material they carry between roll I44 and plate I45, which interval is equal to the time required for pin I30 to travel over the curved dwell surface of lever I3I, after the release of which, spring I35 causes roll I44 to fall and hold the sheet of paper securely in position upon plate I45.

Having released lever I3I, pin I30 on gear 53 next engages lever I46 which imparts an upward impulse to lever I" both of which are pivotally mounted upon boss I34, lever I41 having a laterally projecting lug I48. At the instant that lever I4'I received its upward impulse,

pin 8I fixed upon slidable member 8I, hasreached a point in its travel with arm 13, which is in a juxtaposition to lug I48, the aforementioned upward impulse of which thereupon trips pin 8| and causes attached member 8| to move radially outwardly. The radial outward movemen of slidable member 8|, and, through crank levers 85 and connecting rod' I6, the consequent simultaneous outward radial movement of slidable member 82, results in the opening of paper gripping fingers 18 and 83 to' release the paper, the forward projecting edge of which is already gripped between roll I44 and plate I45. This outward movement of member 82'causes springpressed latch 81 to again engage the notch in member 82, whereupon it is retained in its outward position and the paper gripping fingers 19 and 83 remain open, as is illustrated in Fig. 8.

The extreme forward and upward limit of the movement of the paper carrying arms 13 and 15 is governed by the are through which crank lever 51 is thrown by the movement of roller 56 in its rectilinear groove. Owing to the relative positions of.arc 58 and the pivot point 58 of lever 51 with respect-to the axis 54 of gear 53 and its roller 56, it will be seen that the movement imparted to crank lever 51 during the upward movement of the paper carrying arms 13 and 15 is relatively slow, because of the large angle through which roller 56 moves, and interrupted because of the pause provided for severing the sheet of paper or other material from the web. The slow forward movement of the paper' carrying arms is provided to permit the proper and precise action of the paper carrying, severing and measuring mechanisms, so that the paper carrying cycle is effective and accurate without damage to the sheet material which might result if greater speed were used. However, upon the reversal of the direction of the angular movement of crank lever 51, which is occasioned by the upward movement of roller 56 as it passes to the side ofthe vertical center line of gear 53, it will be seen that the relatively small angle through which roller 56 moves to again reverse the direction of the movement of crank 51, causes a very rapid return movement of crank 51 and the consequent uninterrupted quick return movement of the paper carrying arms 13 and 15 to the original position shown most clearly in Figs. '1 and 8, since accordingly as crank 51 reverses in movement, the rotation of pinion 60 is also reversed. The speed ratio of the quick return movement of the arms 13 and 15 to their slow forward paper feeding movement is approximately four to one. As pinion 60 begins to rotate in the reverse direction, lever 63 moves with it and away from arm 13, since it has been previously unlatched therefrom, until the angle between lever 63 and arm 13 is sufllcient to permit the re-engagement of spring-pressed latch 12 with pin 1|, whereupon, after the resultant pause, lever 63 and arm 13 are again connected by latch 12, and lever 63 pulls arm 13 and consequently arm 15, with it through an uninterrupted return orbit into the original position shown in Figs. 1, 3, 7 and 8, and the paper carrying cycle recommences upon the'timed reversal of oscillating crank 51.

The sheet. material supply consists of two or more separate sources which are disposed in the pedestal of ;the machine, any one of which may be selectively drawn upon at the will of the operator or automatically as desired. By referring particularly to Fig. 3, it will be seen that there are two sheet material supply rolls, I50 and I5I which are primarily mounted upon brackets I52 and I53, respectively. a pair of each of which are secured to and project from the rear of the standards I and 2 constituting the pedestal of the machine. The ends of the axles I54 and I55 of the rolls I50 and I5I are respectively mounted upon two pairs of freely rotatable bearing rollers I56 and I51 respectively attached to the brackets I52 and I53. Each of the supply roll axles I54 and I55 is provided with disc collars I58 and I59, respectively, against which arcuate brake shoes I60 and I6I respectively bear, being pivoted in brackets I52 and I53, whereby the rolls I50 and I5I are prevented from unrolling or overrunning as the sheet material is rapidly drawn therefrom by the machine, the pressure of brake shoes I60 and I 6I being governed by the weight and angle of respective levers I62 and I63. The sheet material webs I50 and I5I pass respectively from supply rolls I50 and HI under tensioning rolls I64 and I65, which are mounted upon levers I66 and I61 pivotally secured upon shafts I68 and- I69, respectively, which are fixed between standards I and 2 of the machine pedestal. Levers I66 and I61 are provided with collinear extensions I10 and "I, upon which are adjustably mounted the respective counterweights I12 and I13, by which the tension of the webs of sheet material may be regulated, since the pressure of rolls I64 and I65 upon the web is thereby variable. Accordingly, the rolls I 64 and I65 are continually hunting to maintain theproper tension of the webs of sheet material passing under them. If, however, the material tends to draw ofl of rolls I50 and I5I too slowly or drags, the consequent tightening of the web raises rolls I 64 and I65, whereupon the cam action of projections I14 and I15 at the bases of levers I62 and I63 and disposed so as to be coplanar with the respective ends of levers I62 and I 63, raises said levers away from shafts I68 and I69, which accordingly releases brake shoes I60 and I 6| from discs I58 and I59 respectively. 'I'hereupon the rolls I50 and I5I are free for readier revolution and the webs may consequently be drawn on more easily until the slack in the web is sufllcient to allow rolls I64 and I65 to assume their normal position as shown in Fig. 3,-

tween side frames 48 and 49 as illustrated more.

clearly in Figs. 3, 7 and 8. The two webs of sheet Fig. 7, and the lateral edge of rear apron material are then threaded between the paper guide aprons I18 and I19, which are respectively shown in Figs. 20 and 19, and certain spaced relatively narrow guide strips I 81 and I90, shown in Figs. 18, 21 and 22, until the forward edges of the webs of sheet material are'even with the top edges of aprons I18 and I19. Referring to Figs. 7 and 18, it will be seen that the aprons I18 and I19 project upwardly in a curve coincident with the arc described by the paper gripping fingers 19 and 83 which are embraced by the inner lateral edge of front apron I18, which is shown so registered in it is in position to register with fingers 19 and 83. The aprons I 18 and I19 are fastened by their lower edges to a I8I, respectively, of the paper switching frame I82, which is suspended from two pairs of parallel motion links I83 and I84, respectively, from tubular shafts I85 and I86 which are journalled at the bottom of side frames 48 and 49, as is most clearly shown in Figs. '7, 8 and 17. Coacting with aprons I 18 and I 19 are the two pairs of guide strips I81 shown in Fig. 21, a pair of each of which are disposed so as to be even with the inner lateral edges of front apron I 18 and with the lateral edges of the apron I19, as well as parallel to the rear surfaces of each so as to form a narrow space frame I82, whereas the guides I81 for rear apron I19 are likewise fastened by their lower ends to brackets I88 which are fixed to another cross-bar I89 of frame I82. A similar guide I90, shown in Fig. 22, is mounted at the centers of and so as to co-act with aprons I18 and I19, the center guide I90 for front apron I18 being mounted at its lower end upon a boss on cross-bar I82, and the center guide I 90 of rear apron I19 being mounted at its lower end upon a boss on cross-bar I89 of frame I82. Journalled in lugs formed on brackets I88 on cross-bar I89 and in like lugs formed on cross-bar I 8| are articulated shafts I 9|, which are so formed, as shown in Fig. 18, as to be self-aligning and flexible within limits to compensate for the unavoidable variations in the web feed and its various guiding systems. Levers I92 are mounted at each end of shafts I9I and carry the ratcheted rollers I93 provided with a series of friction rings I94 for the purpose of smoothing and constraining the web to the aprons I18 and I19 and for restraining the web against being drawn backward by virtue of their ratchets I95 shown-in Figs. 17 and 18. Articulated shafts I9I are each provided with a pair of rigid lever brackets I96 near their ends which co-act with similar rigid extensions in brackets I88 and on cross-bar I8I, between which and aforesaid lever brackets I96 are disposed coil springs I91, which effect the constant pressure of friction rings I94 of rollers I93 against the web of sheet material, which is disposed upon the under surfaces of aprons I18 and I19, as may be readily seen by referring to Figs. 7, l7 and 18.

The sheet material switching system is provided for the purpose of changing the character of the interposed layers of sheet material being wound upon the winding spindle, either before the winding operation has begun, or during the winding operation, when, for instance, it is desired for insulation purposes to have a different type of wire layer separation between the first and last few layers of wire, such as heavy paper,

I19 when pair of like cross bars I80 and oiled linen, silk, or the like. The sheet material switching mechanism may be selectively operated manually or automatically, as desired, and the new material is automatically interposed between the elected wire layers without interruption of the winding process, since the switching can only be done at the proper instant, due to the protective timed mechanism which is to be hereinafter described. As above disclosed, switching frame I82 is suspended by parallel motion links I83 and I84 from shafts I85 and I86, respectively, which are journalled in the side frames 48 and 49 so as to allow the free swing of frame I82 when actuated. Referring particularly to Figs. '7 and 14, it will be seen that a bellcrank lever handle I98 is rigidly fastened to shaft I85, so that any motion of handle I98 causes motion of frame I82, whereas the locking of handle I98 likewise locks frame I82 against any motion. By additional reference to Fig. 9, it will be seen that handle I98 is provided with a circular hole in its elbow, which is adapted to normally register with a slightly elliptical hole near the bottom of side frame 48 and through which a pin I99 is normally inserted, which pin is fitted to and slidable in the hole in handle I98 and pivotally mounted at its end to one end of lever 200, which is fulcrumed between a pair of ears 20I integral with handle I98 and is forced away from handle I98 by a coil spring 202. Accordingly, upon the withdrawal of pin I99 from its engagement with the registering hole in side frame 48 by manually squeezing lever 200 against handle I98 and then pulling upwardly upon handle I98, switching frame I82 may be swung upwardly upon parallel motion links I83 and I84 pivoted on shafts I85 and I86, respectively, until rear apron I19 and its coacting sheet material guiding system register with anvil I29, whereupon paper carrying fingers 19 and 83, upon their return downward movement will embrace the web of sheet material II which is servedv by supply roll I5I, instead of web I50, which had been served by supply roll I50 due to the former position of the switching mechanism, as is best illustrated in Figs. 3 and- '7. However, owing to the fact that the original web I50 of sheet material is being unrolled from roll I50, as shown in Fig. 3, and is moving over front apron I18 and anvil I29, by virtue of being drawn upwardly bythe paper carrying arms 13 and 15, it would be impractical to attempt to switch to another source of sheet material such as web I5I upon apron I19, because of the obvious damage to the webs and to the feeding thereof, if such switching is intended to be done during the winding process. Accordingly, the switching mechanism is locked during the movement of the web of sheet material, but is automatically unlocked when the web stops moving, which occurs only after the knife mechanism has severed the feeding sheet from the web, whereupon both webs I50 and I5I are stationary upon their respective aprons I18 and I19.

Referring now to Figs. '1, 9 and'13, and particularly to Fig. 14, it is apparent that cam I04 controls the locking and unlocking of the switching mechanism, whereby the withdrawal of pin I99 is either prevented or permitted according to the position of cam I04. Follower roller II3 of cam I04 is mounted upon the end of a bell crank 203. fulcrumed upon a pin 204, fixed'in side frame 48, and the other end of bell crank 203, is pivotally attached to the end of a slide member 205 which is slidable in a guide provided takes place, which movement is controlled by cam I04. Accordingly, when cam I04 is shifted along with cams I05 and I06 and gear 55, as heretofore explained and which occasions the severing of the web, follower II3, being released frcm cam I04, causes the slide 205 to move to dis.-

engage the notch in pin I99 so that it may be withdrawn by pressing lever 200 against handle I98, and, by pulling up on handle I98 the material is changed, and pin I99 subsequently registers with and slides into holes 206 in the center of slide 205 and in side frame'48 when handle I 98 is released, whereby the switching mechanism is locked in its other extreme position. A coil spring 201, attached by one end to side frame 48 and by the other end to hell crank 203, tends to maintain the constant pressure cf-follower II3 on cam I04, causes it to drop behind cam I04 when the cam is shifted, and draws slide downwardly to release pin- I99 when cam follower II3 is moved inwardly. Referring to Fig. '7 it is evident that the rotation of cam I04,.during the time of travel of the paper carrying arms 13 and 15 up to the point where they pause for the severing of the web, maintains the switching mechanism looked due to the shape of the cam As the paper carrying arms 13 and 15 begin their forward and upward journey from their extreme lowest position shown in Figs. 3, 7, and 8,

their gripping fingers 19 and 83 embrace but do not grip the lateral edges of the registering one of webs I50 or I5I"-, the leading edges of which are even with the top edges of aprons I18 and I19, respectively. Assuming that the sheet material switching mechanism is arranged as illustrated in the drawings, i. e., so that the fingers 19 and 83 embrace the lateral edges of web I50, which is disposed upon apron I18, the motion of paper-carrying arms 13 and 15 is accompanied by a simultaneous rotation of cam I05, which, owing to the shape of cam edge, causes the lifting of its wiper follower II 4, which pivots about pin II5, pulls link 208 forwardly to turn doublearmed lever 209 about rod 2I0 .fixed in side frames 48 and 49, which effects. the lifting of gripper roller 2 awayfrom anvil I29. Roller 2II is provided with a series of spaced friction rings 2I2, and at one end with a ratchet 2 I3 which permits it to turn in one direction only, i. e., when the web is advancing beneath it, and prevents the web from being drawn backwardly. The other end of shaft 2I0 is provided with a single lever 2| 4 for supporting the other end of roller 2 and another lever 2I5 to which is attached a co l spring 2I6, as shown in Fig. 8, which tends to maintain gripper roller 2 constantly in engagement with anvil I29, maintains a constant pressure of follower II4 upon the cam surface of cam I05, and-also to effect the rapid droppingoff movement of follower II4 from cam I05 as 

